Reciprocating piston fluid powered motor

Abstract

A reciprocating piston fluid powered motor having fluid inlet and outlet, wherein reciprocation is controlled by a reciprocable valve spool communicating with said fluid inlet and outlet and cooperating with a valve slide shiftable on said valve spool to control reciprocation of said valve spool. A needle valve assembly controls the exhaust rate proportionally to the operative speed of the motor.

Description

BACKGROUND OF THE INVENTION

This invention relates to a reciprocating piston fluid powered motor.

Heretofore, motors of this type have included a large cylindrical bore with a piston reciprocable therein responsive to directed air flow. Air flow has been directed by a valve which includes a spool having circumferential O-rings which fit in the bore of a valve housing. Shifting of the spool valve in response to the position of the piston in one direction causes redirection of pressurized inlet air to a port which causes shifting of the piston in the opposite direction. Exhausting of the motors of this type occurs at a port open to atmosphere.

Oftentimes, contamination, resulting from hydrocarbons in the pressure line from a vehicle engine to the fluid powered motor, will fill the clearance gap around the valve spool between the O-rings within the motor valve housing and resist or prevent movement of the valve spool. Also, the O-rings tend to wear, swell, and stick as a result of the contamination which may include a varnish-like substance which results from engine hydrocarbons. The clearance gap also permits leakage of the varnish substance into the motor valve to cause sticking of the valve spool and ultimately inoperability of the motor.

SUMMARY OF THE INVENTION

The fluid powered motor of this invention eliminates the use of a valve spool with O-rings which form chambers for directing air into motor valve ports. The motor of this invention also includes a device for regulating the exhaust air pressure.

Accordingly, it is an object of this invention to provide an improved fluid powered reciprocating piston motor.

Another object is to provide a fluid powered reciprocating piston motor which is reliable in its start-up and high speed operations.

Another object is to provide a motor which reduces or eliminates particle contamination.

Another object is to provide a motor which avoids leakage of contaminant materials into the fluid ports and valve of the motor.

Another object is to provide a motor which operates under high pressures at low speed which, as a result, provides better low-end control of the motor.

Other objects of this invention will become apparent upon a reading of the following description.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of the motor.

FIG. 2 is an end view of the motor.

FIG. 3 is a sectional view of the motor taken along line 3--3 of FIG. 2.

FIG. 4 is a sectional view taken along line 4--4 of FIG. 3.

FIG. 5 is a sectional view taken along line 5--5 of FIG. 3 with portions broken away for purposes of illustration.

FIG. 6 is a sectional view taken along line 6--6 of FIG. 5.

FIG. 7 is a partial sectional view taken along line 7--7 of FIG. 4.

FIG. 8 is a sectional view taken on line 3--3 of FIG. 2 showing air flow and an operational position of the parts and piston opposite the position shown in FIG. 3.

FIG. 9 is a sectional view taken on line 4--4 of FIG. 3 and shows the valve parts in the operational position of FIG. 8.

FIG. 10 is a sectional view taken on line 5--5 of FIG. 3 and shows the parts in the operational position of FIGS. 8 and 9.

FIG. 11 is a partial sectional view taken on line 3--3 of FIG. 2 and shows the return of the parts to the position shown in FIGS. 3 and 4.

FIG. 12 is a partial sectional view taken on line 5--5 of FIG. 3 showing the piston in its extreme position opposite that shown in FIG. 5 and immediately prior to a change of direction.

FIG. 13 is a sectional view taken on line 4--4 of FIG. 3 showing air flow paths and valve part positions for the operational position illustrated in FIG. 12.

FIG. 14 is a partial sectional view taken on line 5--5 of FIG. 3 showing air flow paths as the piston begins movement to the right.

FIG. 15 is an enlarged detail view of a modified exhaust valve assembly shown in a low speed operative position of the motor.

FIG. 16 is an enlarged detail view of a modified exhaust valve assembly shown in a high speed operative position of the motor.

DESCRIPTION OF THE PREFERRED EMBODIMENT

The preferred embodiment illustrated is not intended to be exhaustive or to limit the invention to the precise form disclosed. It is chosen and described to explain the principles of the invention and its application and practical use to thereby enable others skilled in the art to utilize the invention.

The fluid power motor includes a housing 10 which has two complementary cup-shaped housing parts 14 and 16 secured together at their open ends, as by screws 18 extending through laterally projecting end flanges 20 to provide communicating piston bores 48 and 54. A valve housing 22 is secured to motor housing 10 between flanges 20. Motor housing 10 includes a mounting bracket 24 at each end. A motor shaft 26 is journaled in the housing between flanges 20, as by bearings 28. A manifold 75 is provided on valve housing 22.

As seen in FIG. 5, the housing part 14 has formed therein internal passages 30, 32, and housing part 16 has formed therein passages 34 and 36. Seals are provided at 38 between bores 42 and 46 of valve housing 22 and housing part 14 and between bores 40 and 44 of valve housing 22 and housing part 16. Passage 30 communicates with the outer end of piston bore 48 of housing part 14 at a port 50 (FIG. 8). Passage 32 communicates with an intermediate part of bore 48 of housing part 14 at a port 52. Passage 34 communicates with the outer end of piston bore 54 of housing part 16 at a port 56 (FIG. 8) and passage 36 communicates with an intermediate part of bore 54 of housing part 16 at a port 58. Manifold passages 42, 44 connect respectively to manifold ports 39, 41 which, in turn, are open at a lower or interior surface 43 of manifold 75 (FIG. 9). Manifold 75 has a park port 120 formed therein. A shuttle 122 and shuttle seat 124 are positioned within motor valve housing 22 between park port 120 and passages 46 (FIG. 9). A valve housing wall 128 is positioned between passage 46 and park port 120 and valve housing bore 84. A passage 130 (FIGS. 4 and 9) is formed in valve housing wall 128 to place valve housing bore 84 in fluid communication with passage 46 or park port 120 as more fully explained below.

A dual piston unit 60 (FIG. 3) is contained within motor housing 10 and has a cushion 62 at each end. An annular groove is formed in each piston head 60 and receives a sealing ring 64. The intermediate portion 66 of piston unit 60 is narrow and has formed upon it a series of gear teeth 68 defining a rack. Gear teeth 68 mesh with a pinion gear 70 which is fixedly secured to motor shaft 26. Intermediate portion 66 of the piston unit has a planar surface 72. Valve housing 22 has a lower bearing surface 74. Bearing surface 74 slidably engages piston unit surface 72 to insure proper engagement of gear teeth 68 with pinion gear 70 as the piston unit 60 moves within the bores 48, 54. The bores 48, 54 preferably taper slightly toward their outermost ends.

Manifold 75 has a fluid inlet port 76 (FIG. 4) which communicates through an internal passage 78 with a port 80 and a cavity 82 formed in valve housing 22 (FIG. 9) in communication with valve bore 84. A spool valve 86 reciprocates within valve bore 84. Spool valve 86 has two spaced, stepped annular grooves 88 formed therein near its opposite ends which receive seal rings 90. One end of bore 84 has a stop 92 secured therein which limits motion of spool valve 86 in one direction. Spool valve 86 includes a stepped recess 94 at its central portion. A coil spring 96 is seated within recess 94 and a valve slide 98 is also seated in the recess 94 and is pressed by spring 96 against the lower face 43 (FIG. 3) of manifold 75. Valve slide 98 (FIG. 7) fits within cavity 82 and reciprocates with spool valve 86. Valve slide 98 has an upper face 102 which includes offset recesses 104 (FIGS. 4 and 7) which are interconnected by a passage 106. As seen in FIGS. 5 and 10, valve slide recesses 104 and passage 106 alternately interconnect manifold passages 39, 41 with an exhaust port 108 (FIG. 8) in response to directed fluid flow in the operation of motor 10, as more fully described below. Valve slide 98 (FIG. 4) is preferably formed of a material such as Delrin 500 AF, for its wear and self lubricating qualities.

Exhaust port 108 communicates with valve housing cavity 82 (FIG. 4). An exhaust passage 110 (FIG. 3) interconnects port 108 and an exterior exhaust port 112. Exhaust port 112 has a restricted flow passage 114 formed therein (FIG. 8). A needle valve assembly 116 is so positioned in exhaust port 112 that by adjustment of the tension of a spring 118 bearing thereon, assembly 116 controls the pressure within motor 10 by controlling the pressure at which exhaust fluids exit the exhaust port.

Motor 10 will normally be in its inoperative or park position which is shown in FIGS. 3, 4, 5 and 6. In this position, spool valve 86 is seated against stop 92 and piston unit 60 is seated against the end wall of cylinder part 14 as shown in FIG. 3. When motor 10 is in its park position, pressurized air enters both manifold inlet port 76 and park port 120, as indicated by arrows 121 in FIG. 4. Pressurized air entering park port 120 forces shuttle 122 against its seat 124 and flows around the shuttle, through passage 130 and into valve housing bore 84. Air entering manifold inlet port 76 flows around valve slide 98, enters manifold port 41 and flows through bore 44 and passage 34 to port 56 and enters piston bore 54, as indicated by arrows 123 in FIGS. 3 and 5, forcing the piston unit 60 against the end wall of piston bore 48. When piston unit 60 is in its FIG. 3 position, seals 64 expose port 58 (FIG. 5) so that pressurized air from inlet port 76 enters port 58 and flows through passage 36, bore 40 and enters valve housing bore 84 at the end of spool valve 86, as illustrated in FIG. 5 by arrow 121. Pressurized air from park port 120 prevents shifting of spool valve 86.

When reciprocating operation of motor 10 is desired, a control valve (not shown) within a vehicle is shifted to the operating position, thus cutting off flow of pressurized air into park port 120. When the flow of pressurized air from park port 120 ceases, spool valve 86 shifts to the left, as oriented in FIG. 9, in response to pressurized air entering valve housing bore 84 from port 58, as described above. When spool valve 86 is in the position as oriented in FIG. 10, manifold ports 41 and 39 are connected by a recess 104, 106 in the upper face 102 of valve slide 98. As a result, pressurized air from manifold inlet port 76 enters manifold port 39 and flows through manifold bore 42 and passage 30 where it enters piston bore 48 through port 50, as indicated by arrows 125 in FIGS. 8-10. This causes piston unit 60 to shift to the left, as oriented in FIG. 8. As piston unit 60 travels to the left, residual air in piston bore 54 is forced into passage 34 and bore 44 through port 56, as indicated by arrows 127 in FIGS. 8-10. Air exits bore 44 through manifold port 41 and enters manifold exhaust port 108 via valve slide recess 104, as indicated by arrows 127 in FIGS. 8 and 9. Air from exhaust port 108 enters exterior exhaust port 112 where pressure builds up against valve 116 until it overcomes the force of spring 118 and shifts valve 116 to permit air to exit manifold 75 via passage 114. Piston unit 60 continues its leftward travel until port 52 is exposed to pressurized air entering piston bore 48 from port 50. At this time, the pressurized air enters passage 32 and bore 46 whereupon shuttle 122 is unseated and air flows through shuttle seat 124, passage 130, and into valve housing bore 84, as shown by arrows 126 in FIGS. 12 and 13. This shifts spool valve 86 toward the position, as shown in FIG. 13. When valve 86 is so shifted, the right end of the valve chamber 84 is exhausted and residual air in chamber 84 is forced through passage 40, port 38 and passage 36 to exhaust air in chamber 54 and passage 34 (see arrows 127, FIG. 10) to valve port 41 which is interconnected to valve section 104 and external exhaust. (See FIG. 10)

When spool valve 86 is in its rightmost position, as shown in FIGS. 4 and 5, pressurized air from manifold inlet port 76 can no longer enter manifold port 39, but is forced to flow about valve slide 98 within valve housing cavity 82 until it enters manifold port 41, whereupon it flows through bore 44 and passage 34, as shown by arrows 129 in FIGS. 11 and 14. Air which exits passage 34 via port 56 causes piston unit 60 to move to the right. As piston unit 60 moves to the right, residual air in piston bore 48 enters port 50 and flows through passage 30 and bore 42, as indicated by arrows 140 of FIGS. 11 and 14. While spool valve 86 is in its rightmost position, as oriented in FIGS. 4 and 14, manifold ports 39 and 108 communicate via valve slide recesses 104 and passage 106 such that air exiting bore 42 via port 39 will enter port 108 and be exhausted from manifold 75 in the manner described above. As piston unit 60 continues its rightward travel, port 58 is exposed to pressurized air entering piston bore 54 from port 56. This air flows through passage 36 into port 40 whereupon it enters valve housing bore 84 causing spool valve 86 to shift to its leftmost position, as oriented in FIG. 9. This completes an operational cycle of motor 10.

The reciprocating shifting of piston unit 60 causes oscillation of shaft 26 as a result of the interengagement of rack teeth 68 and the pinion gear 70. When it is desired to halt operation of motor 10, the operator manipulates a control valve (not shown) which introduces pressurized air into park port 120 causing shuttle 122 to engage in sealing contact with its seat 124, as described above. This causes the components of motor 10 to come to rest in the position described above and illustrated in FIGS. 3, 4, 5, and 6. If it is desired that piston unit 60 come to rest in its park position at its most leftward position, valve housing 22 and manifold 75 may be mounted upon motor housing 12 in a position the reverse of that shown in FIGS. 4 and 9.

FIGS. 15 and 16 depict needle valve assembly 116 in two of its operative positions. Assembly 116 includes a valve portion 150 having a peripheral recess 156. Valve portion 150 includes shank 155. A flexible O-ring seal 158 is seated in recess 156 and bears against the wall of exhaust port 112. A threaded cap 160 is adjustably secured within exhaust port 112. Spring 118 is positioned in port 112 and abuts cap 160 and valve 150. The position of cap 160 controls the tension which spring 118 exerts on valve 150.

FIG. 15 shows valve assembly 116 in a low speed operating position of the motor. In low-speed operation, exhaust air enters port 112 under a relatively low pressure. Tension from spring 118 acts against the pressure of the exhaust air and urges valve shank 155 into restricted flow passage 114 within which it fits with slight clearance to correlate the amount of air exhausted with the low speed of the motor. In FIG. 16, the motor is in its high speed operative mode, in which the exhaust air enters port 112 at a substantially higher pressure than in the low speed mode. The air pushes against valve head 150 and partially overcomes the tension of spring 118 to cause the tapered end 115 of shank 155 to be withdrawn from passage 114. This action controls the amount of air exhausted during high speed operation of the motor.

The construction of valve 116 permits control of exhaust air in all operative positions of the motor. The exhaust rate may be adjusted by the selective positioning of threaded cap 160 within port 112.

It is to be understood that the invention is not to be limited by the terms of the above description, but may be modified within the scope of the appended claims.

Claims

1. In an oscillatory fluid powered motor including a motor housing formed of two similar cup-shaped parts secured together at their open ends to form an elongated bore, a piston unit having spaced piston heads slidable in said bore, a motor shaft journalled in said housing, drive transmission means connecting said motor shaft and said piston unit for rotationally driving the motor shaft in response to linear motion of the piston unit, said housing parts having complementary passages therein, a valve unit having a housing secured to and transverse of said motor housing bore, said valve housing having a bore, a valve spool slidable in said valve housing bore, said valve housing having passages communicating with said motor housing passages, the improvement comprising a manifold mounted in said valve housing and having a flat face, said manifold having passages formed therein communicating with said motor housing passages, said manifold having a fluid inlet and a fluid outlet, said valve housing having a cavity for communication between said inlet and said valve housing bore, a valve slide mounted in and slidable with said valve spool and fitting within said cavity, said valve slide having a face in sliding contact with a face of said manifold, a face of said valve slide having a passage for selectively connecting said manifold and housing passages with said inlet and said outlet, said manifold passages being so arranged and communicating with said motor housing passages that said valve slide and said piston unit are caused to reciprocate in response to fluid pressure supplied at said inlet, and valve means adjustably positioned adjacent said fluid outlet for exhausting air from said valve spool through said outlet, said valve means including an exhaust port in flow communication with a said valve spool passage, a needle valve slidable in said exhaust port, a cap adjustably positioned in said exhaust port spaced from said needle valve, and resilient means for urging said needle valve towards an outlet flow restricting position in said exhaust port.

2. The motor of claim 1 wherein said exhaust port includes a restricted flow outlet portion, said needle valve including a shank and a body, said shank extending into said exhaust port restricted flow portion with slight clearance under the influence of said resilient means.

3. The motor of claim 2 wherein said motor is selectively operable between two operative speeds, said needle valve controlling the flow rate of exhaust air through said exhaust port proportionally with the selected operative speed of the motor.

4. The motor of claim 1 and seal means associated with said valve spool, said valve spool including a stepped recess accommodating said seal means, said seal means for preventing intermixing of air between said piston chamber and said valve chamber.